EP0197316A2 - Dispositif pour l'amortissement de mouvements - Google Patents
Dispositif pour l'amortissement de mouvements Download PDFInfo
- Publication number
- EP0197316A2 EP0197316A2 EP19860103081 EP86103081A EP0197316A2 EP 0197316 A2 EP0197316 A2 EP 0197316A2 EP 19860103081 EP19860103081 EP 19860103081 EP 86103081 A EP86103081 A EP 86103081A EP 0197316 A2 EP0197316 A2 EP 0197316A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- damper
- damping
- piston
- active
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
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Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
- B60G17/02—Spring characteristics, e.g. mechanical springs and mechanical adjusting means
- B60G17/04—Spring characteristics, e.g. mechanical springs and mechanical adjusting means fluid spring characteristics
- B60G17/0416—Spring characteristics, e.g. mechanical springs and mechanical adjusting means fluid spring characteristics regulated by varying the resiliency of hydropneumatic suspensions
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
- B60G17/015—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load the regulating means comprising electric or electronic elements
- B60G17/0152—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load the regulating means comprising electric or electronic elements characterised by the action on a particular type of suspension unit
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
- B60G17/06—Characteristics of dampers, e.g. mechanical dampers
- B60G17/08—Characteristics of fluid dampers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/10—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using liquid only; using a fluid of which the nature is immaterial
- F16F9/14—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect
- F16F9/16—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts
- F16F9/18—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts with a closed cylinder and a piston separating two or more working spaces therein
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/44—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction
- F16F9/46—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction allowing control from a distance, i.e. location of means for control input being remote from site of valves, e.g. on damper external wall
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/50—Special means providing automatic damping adjustment, i.e. self-adjustment of damping by particular sliding movements of a valve element, other than flexions or displacement of valve discs; Special means providing self-adjustment of spring characteristics
- F16F9/512—Means responsive to load action, i.e. static load on the damper or dynamic fluid pressure changes in the damper, e.g. due to changes in velocity
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2400/00—Indexing codes relating to detected, measured or calculated conditions or factors
- B60G2400/20—Speed
- B60G2400/206—Body oscillation speed; Body vibration frequency
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2400/00—Indexing codes relating to detected, measured or calculated conditions or factors
- B60G2400/60—Load
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2400/00—Indexing codes relating to detected, measured or calculated conditions or factors
- B60G2400/90—Other conditions or factors
- B60G2400/91—Frequency
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2600/00—Indexing codes relating to particular elements, systems or processes used on suspension systems or suspension control systems
- B60G2600/18—Automatic control means
- B60G2600/184—Semi-Active control means
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/8593—Systems
- Y10T137/86493—Multi-way valve unit
- Y10T137/86863—Rotary valve unit
- Y10T137/86871—Plug
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/8593—Systems
- Y10T137/877—With flow control means for branched passages
- Y10T137/87788—With valve or movable deflector at junction
- Y10T137/8782—Rotary valve or deflector
Definitions
- the invention relates to a device for damping movement sequences according to the preamble of the main claim.
- a suspension system has two masses, one mass being one or more wheels of a vehicle and the other mass being the vehicle body, a passive one between the two Normal compression spring arranged, which is referred to as a passive isolator and which is a so-called active damper connected in parallel.
- This damper in which a piston slides in two cylinders dividing it into two working chambers, is considered active because the damping properties, ie the volume displacements, of the pressure medium in the respective working halves of the Damper is actively intervened by control so to speak.
- the two working chambers are each crossed and connected in parallel with one another via oppositely directed valves which only allow a flow of the pressure medium in one direction, in which case the quantity of pressure medium let through by these valves is still actively determined by appropriate control of the valves by means of suitably prepared sensor signals becomes.
- the spring itself is completely passive and the damper has been regarded as active in its properties
- the overall system is referred to in this publication as semi-active or semi-active.
- this designation has no meaningful relation to the dampers relating to the present invention, which are themselves referred to as so-called semi-active dampers without reference to spring systems which have not been taken into account, for reasons which will be discussed further below.
- the invention has for its object to drastically ver the structure of a damper system simple, but on the other hand to design this damper system so that although, as is actually required for certain conditions, active energy is not supplied, a behavior can nevertheless be achieved which essentially integrates the properties of passive damping systems and, at the same time, active damping systems and therefore optimal functionality all conditions are ensured.
- This invention is achieved by the characterizing features of the main claim, with the advantage that once the damping forces are variably adjustable, but also can also be dimensioned asymmetrically in the desired manner so that the damping concept according to the invention is like an active damper or in any case strong approximates how an active damper behaves. No damping forces with a predetermined sign are generated when an active damping force with opposite signs would be required on the basis of the respective operating conditions and sensed sensor signals.
- the damping system according to the invention is designed so that in this case the damping force is zero or almost zero.
- the externally required energy supply relates exclusively to the low control energies that are required, for example, to specify valve positions.
- FIG. 1 shows in the form of a diagram the course of damping amplitude ratios of the main body and wheel over the frequency of the forces acting
- FIG. 2 shows in the form of a diagram the damping force in the so-called V-Vrel plane for the passive damping case, Vrel being the Relative speed of the masses connected to one another via the damper and V represents the bodywork speed applied to a vehicle
- FIG. 3 shows the same diagram as that of FIG. 2, only for the purely active damping case
- FIG. 4 shows the representation of FIGS. 2 and 3 corresponding damping force diagram in the V-Vrel plane for the combined active and passive damping case
- FIG. 5 shows areas in the V-Vrel plane where energy is supplied in the event of damping and where energy is destroyed
- FIG. 6 shows the Course of an effective damping coefficient modulated by sensor signal control in a semi-active damper in the V-Vrel plane once in a perspe 7, the damping force applied by a semi-active damper controlled in terms of its damping force in the V-Vrel plane
- FIG. 8 the same diagram of FIG. 7 when a passive one Damper is only switched on or off
- FIG. 9 shows a first practical embodiment of a semi-active damper with variable, asymmetrical damping behavior in a schematic rule sectional view, together with a diagram indicating the course of the applied damping force over the speed and a further additional image of an alternative embodiment of the Dantyfer valve
- Fig. 10 shows another embodiment of a semi-active damper with direct damping force control by poppet valves, also accompanied by a the course the damping force versus speed diagram
- Fig. 11 shows another embodiment of a semi-active damper with only one cylinder working chamber
- Fig. 12 shows an embodiment of a semi-active damper in which the variable asymmetrical valve mechanisms are housed in the piston
- Fig. 10 shows another embodiment of a semi-active damper with direct damping force control by poppet valves, also accompanied by a the course the damping force versus speed diagram
- Fig. 11 shows another embodiment of a semi-active damper with only one cylinder working chamber
- Fig. 12 shows an embodiment of a
- FIG. 13 shows a variant of the arrangement of the V entilmechanismen in the piston, also in section, and F ig. 14 a, a unidirectional flow of the damping means having damper, Fig. 15, finally, represents the Z u glovessdorfkeit the inventive concepts semi-active damper to a potential, total suspension concept with air suspension.
- V is the so-called body speed, here in the special application, for example, of the motor vehicle body
- v is the wheel speed
- v o is the straight road input speed.
- a passive damper would generate a damping force Fd.
- a passive damping coefficient can be defined in the following equation:
- B A represents the active damping coefficient and Bp the passive damping coefficient
- m and M represent the respective wheel and body masses and k and K the spring constants of the tire or the main suspension.
- curve profiles shown in FIG. 1 show the amplitude relationships (amplitude ratio f) specify above the non-dimensional frequency. It can be seen from FIG. 1 that the wheel and body resonance frequencies are sufficiently well separated, with ⁇ 1 and g2 approximately determining the two resonance peaks in the curves.
- e is the mass ratio m / M and n is the ratio of the undamped and uncoupled natural frequencies
- B1 can be increased by using active body speed feedback, that is B A > o. This enables an increase in ⁇ 1 (or a decrease in body resonance) without loss of body isolation at frequencies above the body resonance frequency. This is particularly favorable for ⁇ 1 ⁇ 2, in the passive case where: is.
- the variables V and Vrel are used as equivalent information to the variables V and v mainly for reasons of simplification, because the variables V and Vrel are in any case easier to measure in practice than V and v.
- FIG. 4 shows the general case of a combined active and passive damping, with B A > o, Bp> o.
- This diagram represents a damping force law that can be implemented by an active force generator that is programmed or controlled to produce a satisfactory generalized form of active damping. This form is called active damping because only velocities appear in the force equation.
- a general active suspension force with state-size feedback also contains terms that include deflections.
- FIG. 5 shows these areas for the case in which B A is somewhat less than Bp.
- Pdiss ⁇ o is always.
- a semi-active damper has the same damping force in all shaded areas how an active system can generate, but for the unshaded areas this is impossible. In other words, this means that in the released, that is, unshaded areas of FIG. 5, each passive or semi-active damper would generate a force with a sign opposite to the active damping force of equation (3).
- One possibility for modulating a semi-active damper is to use a valve in which the opening for the fluid flow (pressure with telzier) is a function of the linear or angular position of a particular element.
- the position of the valve is usually controlled by an electromagnetic transducer. The position can be switched between two extreme values or changed continuously.
- the effective damping coefficient Beff is first defined as follows: whereby, by appropriate actuation of the valve Beff, it is varied continuously, ie with
- FIG. 6 shows how the coefficient Beff must be varied in order to reproduce the damping law given in equation (4) in all the regions of the V-Vrel level in which this is possible.
- danr. Beff set to zero, so Beff ⁇ o, so that a force with the wrong sign is not generated.
- FIG. 7 shows the force generated by an active damper, which is controlled in such a way that the force law specified in FIG. 4 is fulfilled whenever possible. If the variable damping coefficient given in the diagram of FIG. 6 can be realized exactly, then this would be the result. However, this force law can also be implemented more directly by designing a valve mechanism in which the force is controlled directly.
- FIG. 10 which is explained in more detail below, in which an electromagnetically controlled force is supplied to poppet valves which control the cylinder pressure almost independently of the flow.
- a force boost is installed in the ratio of piston to valve area.
- the check valves prevent the generation of forces with the wrong sign, so that the frequency dependence of the electromagnetic force generators need not necessarily be particularly high.
- FIG. 8 shows a simplified system in which a passive damper is simply switched on and off on the basis of the active damper control law.
- the result is a passive system that is always switched off when the active damping force has a sign that is opposite to that which can be generated passively.
- the influence of the velocity V on the damper force Fd is not present in most areas of the V-Vrel level, but the semi-active damper becomes simple in the areas in which the active system would supply energy while a passive energy would destroy it switched off.
- studies, in particular on the basis of computer simulation models and also in practical operation have shown that even this simplified diagram of FIG. 8 has considerable advantages overall. It should also be noted that all of the following exemplary embodiments can be operated by semi-active dampers in this way.
- the damping force is controlled by evaluating, preferably, the speed data V, that is to say, in the application example on motor vehicle suspensions, the absolute speed of the body, which can be measured in a suitable manner by measurement, for example by means of acceleration sensors and subsequent integration, and the relative speed Vrel between body and wheel, which can also be measured in a suitable manner, for example in that, as is known per se, the signals from position detectors on the wheel and body or the displacement path of the damper movement or the like are detected.
- the speed data V that is to say, in the application example on motor vehicle suspensions
- the absolute speed of the body which can be measured in a suitable manner by measurement, for example by means of acceleration sensors and subsequent integration
- the relative speed Vrel between body and wheel which can also be measured in a suitable manner, for example in that, as is known per se, the signals from position detectors on the wheel and body or the displacement path of the damper movement or the like are detected.
- the semi-active shock absorber shown in FIG. 9 can be arranged between a vehicle axle (not shown) and a vehicle body (not shown) and basically consists of a cylinder unit 10 and a piston 11 sliding therein, two working chambers 12a and 12b being formed which are separated by the piston and of course vary in volume when the damper is working.
- the piston is carried by a piston rod 11a, which can be attached to the vehicle body, for example, then the cylinder 10 is arranged on the vehicle axle.
- the two working chambers 12a and 12b are via a respective line 14a, 14b, which (again, connected to branch lines 14a 'and 14a "and 14b' and 14b 'divide for example with a hydropneumatic accumulator 15 namely via the branch lines 14a' and 14b '), wherein there are also check valves 16a, 16b in each of these branch lines, which are designed as spring-loaded ball valves and when there is a pressure medium flow or fluid flow lock out the respective assigned working chamber (for example to the memory).
- the two branch lines 14a ', 14b' merge at 17; the two other branch lines 14a "and 14b" form input or output pressure lines to a variable-asymmetrical damping valve 18 which, via the connection point 17 with a further line 19, also with the accumulator 15 or the two other branch lines 14a ', 14b' is connected.
- the asymmetrical damper valve consists of a valve member 21, which is axially slidably slidable in a cylindrical bore 20 and is likewise essentially cylindrical in shape, but with a central constriction 22 which merges with the adjacent sliding surfaces, for example in a truncated cone shape.
- the two valve connections 23a and 23b connected to the branch lines 14a "and 14b" on the same side are offset in height in the valve member actuating movement; the other valve connection 19 is arranged centrally.
- the function of the damper shown in Fig. 9 is such that, at any position of the valve member 21 in one direction, for example when the shock absorber is compressed when hitting an obstacle, via the branch line 14b "pressure medium via the valve with a predetermined assumed Valve resistance and therefore corresponding damping resistance in line 19 and from this via the check valve 16a can flow to the other working chamber, which should correspond to an assumed positive damping force.
- the check valve 16b in this case enables the piston-cylinder unit to be quickly pulled apart, since in this case the pressure medium from the upper working chamber 12a in the drawing plane is greater than that because of it Asymmetry in this case and in the maintained position practically resistance-free damper valve 18 and can flow into the other chamber via the check valve 16b.
- the displaceability of the valve member 21 then results in the variable asymmetrical damping possibility.
- Such a semi-active damper is therefore able to generate the (non-linear) damping force curves plotted above the speed in the small diagram at the top right, whereby curves of the same shape, i.e.
- variable asymmetrical damper valve 18 is accessible to a variety of variations;
- the valve member 21 ' can also be in the lower right as in the damper valve 18' Corner of the drawing of Figure 9 be formed; the actuating movement is then a rotation x ', and it can be seen from the transitional surfaces 24 which run obliquely on both sides in the same direction that the valve ensures asymmetrical behavior, which basically means that the two valve connections 23a, 23b contribute to the connection 19 on the other side experience a different flow resistance at a given valve member position, generally speaking the valve for the two connections 23a, 23b has different opening cross sections in each position (with the exception of the middle position).
- valve resistance is determined by the valve position.
- the dampers or control valves can simply be switched over as a result of the signal supplied, the signal being, for example, the measurement result of the absolute build-up speed. Continuous changes in the valve resistance or the generated damper force are possible through force feedback circuits. It is an essential feature of the illustrated exemplary embodiments that check valves are provided in connection with the basic valve mechanism, that is to say with the damper valve, so that the valve area can generally be made as intelligent as possible.
- regions 18a ′, 18b ′ of the damper valve are arranged here, each of which represents a poppet valve, in which case the valve inlet or outlet 27 is, for example, directly Electromagnetically controlled forces are applied, which move the valve plate 28 to abut (closure of the sub-valve) or to lift off (opening of the sub-valve).
- the upper partial valve 18a ' is directed for tensile forces acting on the damper and their damping and the lower part is directed towards acting pressure forces.
- the electromagnetically generated push or pull control forces are hydraulically amplified here.
- FIG. 11 represents a pressure medium control option which is only connected to a working chamber 12 ', a pressure line 29 extending from the working chamber 12' being divided into two sub-lines 29 'and 29 ", in each of which a check valve 16a', 16b ', which are connected in series with a damper valve 18', which, with the same designation, is therefore also constructed in the same way as the alternative valve design in the exemplary embodiment of Fig. 9, with the same effects line 30 is connected to the hydropneumatic reservoir or reservoir 15; a branch line 31 can be connected to a load leveling device (not shown).
- FIGS. 12 and 13 differ from the previously explained exemplary embodiments in that the entire valve mechanism (check valves and variably asymmetrical damper valve) is arranged in the piston of the damper.
- the piston is designated 32; it contains passages 33a, 33b on both sides which open into the working chambers 12a, 12b and lead to a damper valve 18 ', which corresponds in its basic structure and in its mode of operation to the damper valve 18' with a rotating element already explained in FIG. 9, for which purpose one Control rod 33 is provided which passes through the piston and piston rod 34 and is guided to a drive member 35.
- the check valves still required here are referred to as simple flap valves with 36a, 36b; they connect the one damper valve connection 37 to the two working chambers 1.2a, 12b and, at the same time, to the external hydropneumatic accumulator 15 via a line 38 initially running in the interior of the piston rod.
- the basic mode of operation of this exemplary embodiment corresponds to that explained above; a check valve and one of the passages of the variable asymmetrical damper valve 18 'must always be passed for each pressure medium flow direction, so that here too the different Damper forces shown in the graphs result.
- the valve mechanism shown in FIG. 13 also corresponds in principle to the valve mechanism of FIG. 12, with the exception that here the damper valve 18 "also contains a rotary valve member 39, but is designed for low pressure with a high flow rate at the same time the respective work spaces 12a, 12b connecting lines to the damper valve are designated 40a, 40b; they each open into ring recesses in the structure of the piston 32 '; these ring recesses are designed so that they have windows which, depending on the angular position of the rotary valve member 39 are either directed at window-like passage openings 41 running over the circumference of the rotary valve, for example in the form of a pot or sleeve (valve open), or are offset with respect to these passage openings, so that the valve is blocked, at least for this connection area Valve behavior are now the on the different ring recesses 42a, 42b in the piston directed passage window rows in the rotary valve member 39 offset from each other, which can be seen from the drawing when comparing the upper window to the lower one.
- the check valves can simply have resilient flaps 44a, 44b on both Piston sides, which close or open a common side channel 45 in the piston, depending on the piston movement, this channel 45 being connected to the one (common) connection 43 of the damper valve 18 "; via a central passage opening 38 in the piston rod, the connection to the hydropneumatic accumulator 15, not shown in this exemplary embodiment, is then also provided.
- This unidirectional flux damper with an electromechanical valve consists of a cylinder 47 and a piston 48 sliding therein with a piston rod 48a.
- the cylinder has an annular, double-walled design and therefore contains an annular chamber 49, which is connected to the lower working chamber 12b 'via first simple resilient bottom flap valves (check valves - can also be designed in one piece).
- a further check valve 50 formed by a spring-preloaded ball, is arranged in the piston, which opens when the piston moves downward and thus connects the lower working chamber 12b 'to the upper working chamber 12a'.
- the damper valve 51 is designed as an electrodynamic slide ring valve, the magnetic part not being shown and thus closing or opening an annular passage opening 52 which connects the upper working space 12a 'to the annular chamber 49, and, as indicated at 53, a medium separation for volume compensation is provided in the upper
- Part 49a of the annular chamber can, for example, be air or another gaseous medium as pressure medium, pressure oil in the lower part.
- the M is ODU lation of the damping force in this embodiment in Fig controlled by the Gleitringventil 51. 14; the valve must be designed so that it can open very quickly whenever the relative speed is such that the sign of the damping force developed is opposite to the damping force required by the control device. Otherwise the sign of the relative speed is always such that the damper can generate the force desired by the control device. In this case the valve can be controlled with or without force feedback.
- This valve has advantages due to the unidirectional medium (oil) flow; therefore, the oil can be filtered to remove contaminants - valve clamps are avoided. The heat transfer is also improved with this damper.
- Such semi-active dampers with variable asymmetrical damper behavior can be used, for example, in suspension systems of the type shown schematically in FIG. 15; 15 uses air or another gaseous medium as the pressure medium and contains, as an essential element, a pressure chamber 55, in which a bellows 57 moved by a piston plate 56 rolls.
- the piston plate 56 connects the wheel mass 59 to the body mass 60 of a vehicle, for example, via a piston rod 58; the pressure chamber 55 is contained in the assembly dimensions.
- the pressure chamber 55 is connected via a change-over valve 60 to a mechanism 61 which determines the suspension properties of the suspension system and which contains an actuating piston 63 in a cylinder device 62 which, by controlled drive from the outside, for example via sensor signals Acceleration, driving speed, steering angle, road condition and. Like. Following, is adjusted axially. whereby the suspension hardness of the system can be specified depending on the position of the piston 63. If there is no control drive for the piston 63, a blocking device 64 ensures that the piston stops, so that the suspension hardness remains essentially constant. The piston 63 sits with a certain leakage clearance A23 in the cylinder unit, so that there is a static pressure equalization.
- the pressure chamber 55 is connected to a load balancing device via a line 65, a control valve 66 being provided which connects the line 65 either to a pressure medium supply line 67 or to a drain line 68.
- a damping device as explained further above and as it is denoted by 69 in FIG. 15. It is then possible to use from the large number of signals obtained for setting the suspension hardness, for example via appropriate sensors, if necessary after appropriate preparation, for setting the damper valve or generally for damper control, or vice versa, position signals also acting on the load balancing device at the same time can.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Vehicle Body Suspensions (AREA)
- Fluid-Damping Devices (AREA)
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE3513128 | 1985-04-12 | ||
DE3513128 | 1985-04-12 | ||
DE19853524862 DE3524862A1 (de) | 1985-04-12 | 1985-07-12 | Vorrichtung zur daempfung von bewegungsablaeufen |
DE3524862 | 1985-07-12 |
Publications (3)
Publication Number | Publication Date |
---|---|
EP0197316A2 true EP0197316A2 (fr) | 1986-10-15 |
EP0197316A3 EP0197316A3 (en) | 1987-05-27 |
EP0197316B1 EP0197316B1 (fr) | 1992-04-01 |
Family
ID=25831252
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP19860103081 Expired - Lifetime EP0197316B1 (fr) | 1985-04-12 | 1986-03-07 | Dispositif pour l'amortissement de mouvements |
Country Status (3)
Country | Link |
---|---|
US (2) | US4936423A (fr) |
EP (1) | EP0197316B1 (fr) |
DE (2) | DE3524862A1 (fr) |
Cited By (26)
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EP0279507A2 (fr) * | 1987-01-20 | 1988-08-24 | Ford Motor Company Limited | Système de contrôle pour dispositif de suspension de véhicule automobile |
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EP0302587A2 (fr) * | 1987-08-05 | 1989-02-08 | Lord Corporation | Amortisseur semi-actif pour véhicules et similaires |
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Cited By (39)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0211173A3 (en) * | 1985-07-31 | 1989-01-11 | Barry Wright Corporation | Active vibration isolation system employing electro-rheological fluid |
EP0211173A2 (fr) * | 1985-07-31 | 1987-02-25 | Barry Wright Corporation | Système d'isolation active contre les vibrations utilisant un fluide électro-rhéologique |
EP0221486A2 (fr) * | 1985-10-26 | 1987-05-13 | Toyota Jidosha Kabushiki Kaisha | Système de commande d'un amortisseur |
EP0221486A3 (en) * | 1985-10-26 | 1987-08-26 | Toyota Jidosha Kabushiki Kaisha | Shock absorber controller |
US4756549A (en) * | 1985-10-26 | 1988-07-12 | Toyota Jidosha Kabushiki Kaisha | Shock absorber controller |
EP0243613A1 (fr) * | 1986-04-02 | 1987-11-04 | Robert Bosch Gmbh | Dispositif pour l'amortissement de mouvements |
EP0270893A2 (fr) * | 1986-12-09 | 1988-06-15 | Robert Bosch Gmbh | Dispositif pour le contrôle actif des suspensions de véhicules automobiles |
EP0270893A3 (en) * | 1986-12-09 | 1989-01-04 | Robert Bosch Gmbh | Device for the active control of motor vehicle suspensions |
FR2609129A1 (fr) * | 1986-12-24 | 1988-07-01 | Bosch Gmbh Robert | Dispositif pour amortir des mouvements, notamment ceux de la suspension d'une automobile |
EP0279507A3 (fr) * | 1987-01-20 | 1989-10-25 | Ford Motor Company Limited | Système de contrôle pour dispositif de suspension de véhicule automobile |
EP0279507A2 (fr) * | 1987-01-20 | 1988-08-24 | Ford Motor Company Limited | Système de contrôle pour dispositif de suspension de véhicule automobile |
EP0300204A2 (fr) * | 1987-07-22 | 1989-01-25 | Robert Bosch Gmbh | Amortisseur |
EP0300204A3 (en) * | 1987-07-22 | 1990-05-16 | Robert Bosch Gmbh | Damper |
EP0302587A3 (fr) * | 1987-08-05 | 1989-10-04 | Lord Corporation | Amortisseur semi-actif pour véhicules et similaires |
EP0302587A2 (fr) * | 1987-08-05 | 1989-02-08 | Lord Corporation | Amortisseur semi-actif pour véhicules et similaires |
EP0304801A2 (fr) * | 1987-08-25 | 1989-03-01 | Trw Inc. | Jambe de suspension à taux d'amortissement variable réglé |
EP0304801A3 (en) * | 1987-08-25 | 1989-10-11 | Trw Inc. | Strut with controlled variable damping rate |
EP0326238A2 (fr) * | 1988-01-29 | 1989-08-02 | Lord Corporation | Montage de clapet de piston d'un amortisseur semi-actif |
EP0326238A3 (fr) * | 1988-01-29 | 1990-04-04 | Lord Corporation | Montage de clapet de piston d'un amortisseur semi-actif |
FR2635298A1 (fr) * | 1988-07-07 | 1990-02-16 | Bosch Gmbh Robert | Suspension pour vehicules possedant une jambe de suspension entre la carrosserie et un essieu |
DE3837863C1 (fr) * | 1988-11-08 | 1990-03-01 | Daimler-Benz Aktiengesellschaft, 7000 Stuttgart, De | |
EP0367949B1 (fr) * | 1988-11-08 | 1993-05-19 | Daimler-Benz Aktiengesellschaft | Système de suspension pour véhicules |
EP0367949A2 (fr) * | 1988-11-08 | 1990-05-16 | Daimler-Benz Aktiengesellschaft | Système de suspension pour véhicules |
WO1990014970A1 (fr) * | 1989-06-08 | 1990-12-13 | Robert Bosch Gmbh | Procede et dispositif pour amortir des sequences de mouvement |
EP0403803A1 (fr) * | 1989-06-20 | 1990-12-27 | AUGUST BILSTEIN GMBH & CO. KG | Suspension semi-active |
WO1991000187A1 (fr) * | 1989-06-29 | 1991-01-10 | Robert Bosch Gmbh | Reglage semi-actif du chassis |
WO1991006439A1 (fr) * | 1989-10-24 | 1991-05-16 | Robert Bosch Gmbh | Procede et dispositif pour la regulation du chassis |
FR2660386A1 (fr) * | 1990-03-30 | 1991-10-04 | Oustaloup Alain | Nouveau systeme de suspension. |
FR2665670A1 (fr) * | 1990-08-07 | 1992-02-14 | Bosch Gmbh Robert | Dispositif pour amortir des phases de mouvement. |
DE4117897C2 (de) * | 1991-05-31 | 2001-10-04 | Bosch Gmbh Robert | System zur Erzeugung von Signalen zur Steuerung oder Regelung eines in seinen Bewegungsabläufen steuerbaren oder regelbaren Fahrwerkes |
EP0591754A1 (fr) * | 1992-10-07 | 1994-04-13 | Toyota Jidosha Kabushiki Kaisha | Dispositif de commande de l'attitude de la carrosserie d'un véhicule |
EP1657469A1 (fr) * | 2004-11-11 | 2006-05-17 | Zf Friedrichshafen Ag | Amortisseur de vibrations avec force d'amortissement variable |
EP1659310A3 (fr) * | 2004-11-18 | 2006-11-15 | Öhlins Racing Ab | Amortisseur (de choc) pour véhicules |
US7607522B2 (en) | 2004-11-18 | 2009-10-27 | öHLINS RACING AB | Shock absorber for vehicles |
US7823895B2 (en) | 2007-11-23 | 2010-11-02 | Stromsholmen Ab | Suspension system, vehicle comprising such a suspension system and a method for controlling a suspension system |
US8398091B2 (en) | 2008-05-15 | 2013-03-19 | Toyota Jidosha Kabushiki Kaisha | Suspension system for vehicle |
WO2016037736A1 (fr) * | 2014-09-09 | 2016-03-17 | Robert Bosch Gmbh | Ensemble d'accouplement de masse pour véhicule |
US9987914B2 (en) | 2014-09-09 | 2018-06-05 | Robert Bosch Gmbh | Mass-coupling arrangement for a vehicle |
DE102015214604A1 (de) * | 2015-07-31 | 2017-02-02 | Bayerische Motoren Werke Aktiengesellschaft | Hydraulische Zylinder-Kolbeneinheit, insbesondere Einrohr-Dämpfer |
Also Published As
Publication number | Publication date |
---|---|
EP0197316B1 (fr) | 1992-04-01 |
US4936423A (en) | 1990-06-26 |
DE3524862A1 (de) | 1986-10-30 |
US5024302A (en) | 1991-06-18 |
DE3684628D1 (de) | 1992-05-07 |
EP0197316A3 (en) | 1987-05-27 |
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